EP1338449B1 - Vehicle air conditioning system, especially CO2-air conditioning system - Google Patents

Vehicle air conditioning system, especially CO2-air conditioning system Download PDF

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Publication number
EP1338449B1
EP1338449B1 EP03003752A EP03003752A EP1338449B1 EP 1338449 B1 EP1338449 B1 EP 1338449B1 EP 03003752 A EP03003752 A EP 03003752A EP 03003752 A EP03003752 A EP 03003752A EP 1338449 B1 EP1338449 B1 EP 1338449B1
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EP
European Patent Office
Prior art keywords
heat exchanger
coolant
conditioning system
expansion valve
valve
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
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EP03003752A
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German (de)
French (fr)
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EP1338449A1 (en
Inventor
Ullrich Dr. Hesse
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Valeo Compressor Europe GmbH
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Zexel Valeo Compressor Europe GmbH
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Publication of EP1338449A1 publication Critical patent/EP1338449A1/en
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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/02—Heating, cooling or ventilating [HVAC] devices the heat being derived from the propulsion plant
    • B60H1/04—Heating, cooling or ventilating [HVAC] devices the heat being derived from the propulsion plant from cooling liquid of the plant
    • B60H1/08—Heating, cooling or ventilating [HVAC] devices the heat being derived from the propulsion plant from cooling liquid of the plant from other radiator than main radiator
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/32—Cooling devices
    • B60H1/3204—Cooling devices using compression
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/39—Dispositions with two or more expansion means arranged in series, i.e. multi-stage expansion, on a refrigerant line leading to the same evaporator
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B6/00—Compression machines, plants or systems, with several condenser circuits
    • F25B6/04—Compression machines, plants or systems, with several condenser circuits arranged in series
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide

Definitions

  • the invention relates to a vehicle air conditioning according to the preamble of claim 1
  • Air conditioners can also be used as additional heating, i. operate in so-called heat pump circuit. This means of course a function reversal of conventional air conditioning systems, where as Refrigerant R 134a is used.
  • the operation of conventional Air conditioning in heat pump circuit has a relatively high Circuit and control effort result. Furthermore, it is the heat output, especially at very low outside temperatures, Unsatisfactory, since the evaporation pressure due to temperature decreases to the negative pressure range. This will be the Suction density and converted power correspondingly low.
  • the starting point of a corresponding air conditioning system is the conventional heating circuit of a vehicle on the one hand and the refrigerant circuit of a CO 2 air conditioning system on the other hand according to FIG 7.
  • FIG 7 shows a possible arrangement for the heating circuit of a motor vehicle and the system scheme or the refrigerant circuit of a CO 2 air conditioning, which is designed solely for a cooling operation.
  • the heating circuit comprises an engine 1, a heating heat exchanger 2, a circulation pump 3, which is usually the main water pump of the engine 1, and a two-way valve 4.
  • For the refrigeration cycle are essential components with an evaporator 5, a compressor 6, a refrigerant cooler 7, an inner heat exchanger 8 and an expansion valve 9 are shown.
  • the heating heat exchanger 2 can be bridged by a by-pass line, wherein the two-way valve 4 is arranged between this by-pass line and the heating heat exchanger 2, in particular heating heat exchanger. By appropriate switching of this valve, the cooling water can be passed either through the heating heat exchanger 2 or on this.
  • a heating operation is with the above-described air conditioner not possible according to FIG.
  • An air conditioner that except for cooling the passenger compartment in the Summer can also be used as heating is from the DE 100 06 513 A1, which forms the basis for the preamble of Patent claim 1 forms known.
  • the air conditioning according to the DE 100 06 513 A1 essentially comprises a compressor, a Refrigerant cooler, an internal heat exchanger between coolant cooler and evaporator side, an expansion valve and a Evaporator, wherein to switch the air conditioning from the cooling mode in the heating mode with an engine-side cooling circuit integrated additional heat exchanger integrated is.
  • the additional heat exchanger is an expansion valve downstream, by means of the heating mode Refrigerant can be throttled to a lower pressure.
  • the present Invention Based on this prior art is the present Invention, the object of a structurally simple as possible Specify a solution for bridging the expansion valve, the air conditioning is easily converted by a cooling operation in a heating mode and vice versa is switchable.
  • An essential point of the invention is therefore that a By-pass line in front of one arranged in the refrigerant line Shut off valve and connected to the input side of Compressor immediately, i. Bridging the rest Refrigerant circuit is fluidly connected. This is a constructive simple solution of the problem underlying the invention guaranteed.
  • the air conditioning system of Figure 1 is compared to the prior art of Figure 3 modified to the effect that a heating operation with the then operating as a heat pump air conditioning is possible.
  • an additional heat exchanger 10 is provided, which is integrated for deheating the gaseous refrigerant and for transferring the heat to a cooling water circuit.
  • the cooling water circuit is identified by the reference numeral 17.
  • the additional heat exchanger 10 so there is a heat exchange between the refrigerant circuit on the one hand and motor-side cooling water circuit on the other.
  • the heated to high temperature refrigerant, namely CO 2 comes from the heat exchanger 10 upstream compressor 6.
  • the additional heat exchanger 10 is followed by an expansion valve 14, by means of which the refrigerant can be throttled to a lower pressure during heating operation.
  • the expansion valve 14 is in a by-pass line, which branches off from the refrigerant line 13 between the additional heat exchanger 10 and the refrigerant cooler 7.
  • This by-pass line is identified by the reference numeral 15. It is connected in parallel to the aforementioned coolant line while bridging a shut-off valve 11 arranged in the latter.
  • the shut-off valve 11 serves to shut off the free refrigerant passage between the additional heat exchanger 10 and refrigerant radiator 7.
  • the expansion valve 14 is effective, by which the pressure of the refrigerant is throttled so far that serving as a refrigerant radiator in the climate case heat exchanger 7 absorbs heat in heat pump mode as an evaporator ambient heat.
  • the mode of operation in heating mode is as follows:
  • the compressor 6 compresses the refrigerant, namely CO 2 , to a high final pressure of about 80-120 bar.
  • the compression end temperatures are deliberately kept high, so that sufficient heat can be transferred to the motor side heating water circuit 17 in the additional heat exchanger 10, which then the heating heat exchanger 2 is supplied to the passenger compartment.
  • the refrigerant, ie CO 2 is throttled by the additional heat exchanger 10 downstream expansion valve 14 to a lower pressure of, for example, about 20 bar in the wet steam area and evaporates in the refrigerant cooler 7 at lower temperatures.
  • the refrigerant absorbs environmental heat.
  • the inner heat exchanger 8 and the evaporator 5 are flowed through without appreciable heat exchange.
  • the valve 12 is flowed through virtually without pressure loss and thus without pressure change.
  • the refrigerant evaporates and thus absorbs heat from the ambient air, which is supplied to the passenger compartment.
  • the suction gas is superheated and fed to the compressor 6.
  • the refrigerant is compressed to a pressure of eg 70-120 bar and reaches a final compression temperature of up to and above 150 ° C.
  • the refrigerant is then re-enticed in the additional heat exchanger 10 and flows through the open shut-off valve 11 into the downstream refrigerant cooler 7, namely pre-cooled energetically, so that only a proportionate cooling of the refrigerant must be carried out in the refrigerant cooler 7.
  • the refrigerant is then further subcooled in the inner heat exchanger and throttled expansion valve 9 to the evaporation pressure.
  • the shut-off valve 12 in the by-pass line 18 is closed.
  • both the additional heat exchanger 10 and the refrigerant cooler 7 are available for cooling the refrigerant or CO 2 gas.
  • the cooling operation is energetically cheaper than in a pure cooling circuit of Figure 3.
  • This side effect can be used to use a cheaper refrigerant radiator or to improve the energy efficiency of the entire system.
  • the heat that is transferred from the additional heat exchanger 10 to the cooling water circuit 17, can be in the bypass pass to the heating heat exchanger 2 directly to the engine 1. During warm-up, at low loads and during warm-up, this heat serves to keep the engine at an energy-efficient operating temperature and thereby save fuel. If the engine is warm, the heat is dissipated via the engine radiator not shown here.
  • Residual heat that does not transfer to the passenger compartment in heating mode is used in cold engine, this in addition to heat up and into an energetically favorable operating point bring.
  • the variant according to Figure 2 is characterized in that of the refrigerant line 13 between additional heat exchanger 10 and refrigerant cooler 7 branches off a by-pass line 15, in front of a disposed in the mentioned refrigerant line 13 Shut-off valve 11.
  • the by-pass line 15 is connected to the Input side of the compressor 6 directly, i. under bridging the other coolant circuit fluidly connected.
  • Expansion valve 9 between the inner heat exchanger 8 and Evaporator 5 it is not necessary to further Expansion valve 9 between the inner heat exchanger 8 and Evaporator 5 to bridge.
  • an expansion valve 16 is arranged in the by-pass line 15, an expansion valve 16 is arranged.
  • the embodiment of Figure 2 is characterized by a hot gas bypass circuit in heating operation conditionally through the direct connection between the refrigerant outlet the additional heat exchanger 10 and the input of the Compressor 6.
  • the votes in the additional heat exchanger 10 Power corresponds to the power absorbed by the compressor 6.
  • the expansion valve 16 must during be closed normal cooling operation.
  • the by-pass line 15 in the embodiment of Figure 2 as Capillary perform that has a sufficient throttle effect. In this case, it would suffice for the valve 16 a easy to use shut-off valve. As already mentioned, can on the shut-off valve 12 for bypassing the expansion valve.
  • valves can be in the circuits described also specifically to realize a dehumidifying operation in which the Evaporator 5 dehumidified and reheated 2 heat exchanger becomes.
  • shut-off valves can of course also in intermediate positions be brought depending on the desired operating condition.
  • FIGS. 5 and 6 To safely avoid problems with the flow through the Evaporator 5 under heating operation in the embodiment according to FIG. 1, in FIGS. 5 and 6, is a bypass of the evaporator 5 intended.
  • the by-pass line 18 with by-pass valve 12 bridged either the inner heat exchanger 8 and evaporator. 5 ( Figure 5) or the expansion valve and evaporator 5 ( Figure 6), So in any case, the evaporator. 5

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • General Engineering & Computer Science (AREA)
  • Air-Conditioning For Vehicles (AREA)

Description

Die Erfindung betrifft eine Fahrzeugklimaanlage gemäß dem Oberbegriff des Patentanspruchs 1.The invention relates to a vehicle air conditioning according to the preamble of claim 1

Fahrzeugklimaanlagen dienen primär zur Kühlung des Fahrgastraumes im Sommer. Für den Winterbetrieb sind Klimaanlagen meist nicht geeignet. Dabei zeigt sich, daß moderne Fahrzeuge mit verbrauchsarmen Motoren im Winter eine unbefriedigende Heizleistung aufweisen. Zur Abhilfe werden insbesondere bei diesen Fahrzeugen Zusatzheizungen serienmäßig eingebaut. Grundsätzlich lassen sich auch Klimaanlagen als Zusatzheizung einsetzen, d.h. in sog. Wärmepumpenschaltung betreiben. Dies bedeutet natürlich eine Funktionsumkehr herkömmlicher Klimaanlagen, bei denen als Kältemittel R 134a verwendet wird. Der Betrieb herkömmlicher Klimaanlagen in Wärmepumpenschaltung hat einen relativ hohen Schaltungs- und Steuerungsaufwand zur Folge. Des weiteren ist die Heizleistung, insbesondere bei sehr niedrigen Außentemperaturen, unbefriedigend, da der Verdampfungsdruck temperaturbedingt bis in den Unterdruckbereich absinkt. Damit werden die Saugdichte und umgesetzte Leistung entsprechend gering. Vehicle air conditioning systems are primarily used to cool the passenger compartment in summer. For winter operation, air conditioning systems are usually not suitable. It turns out that modern vehicles with low-consumption engines in winter unsatisfactory heating power exhibit. To remedy this particular Vehicles additional heaters installed as standard. in principle Air conditioners can also be used as additional heating, i. operate in so-called heat pump circuit. This means of course a function reversal of conventional air conditioning systems, where as Refrigerant R 134a is used. The operation of conventional Air conditioning in heat pump circuit has a relatively high Circuit and control effort result. Furthermore, it is the heat output, especially at very low outside temperatures, Unsatisfactory, since the evaporation pressure due to temperature decreases to the negative pressure range. This will be the Suction density and converted power correspondingly low.

Bei Einsatz von CO2 als Kältemittel lassen sich günstigere Voraussetzungen schaffen. Untersuchungen haben gezeigt, daß im Wärmepumpenbetrieb mit CO2 sich hohe Heizleistungen erzielen lassen. Des weiteren ist der Schaltungsaufwand erheblich einfacher als bei R 134a-Klimaanlagen.When using CO 2 as a refrigerant can create more favorable conditions. Investigations have shown that high heat outputs can be achieved in heat pump operation with CO 2 . Furthermore, the circuit complexity is much easier than R 134a air conditioners.

Der Ausgangspunkt einer entsprechenden Klimaanlage ist der herkömmliche Heizkreislauf eines Fahrzeugs einerseits und Kältemittelkreislauf einer CO2-Klimaanlage andererseits entsprechend Figur 7. Figur 7 zeigt eine mögliche Anordnung für den Heizkreislauf eines Kraftfahrzeuges und das Anlagen-Schema bzw. den Kältemittelkreislauf einer CO2-Klimaanlage, die allein für einen Kühlbetrieb ausgelegt ist. Der Heizkreislauf umfasst einen Motor 1, einen Heizwärmetauscher 2, eine Umwälzpumpe 3, bei der es sich üblicherweise um die Hauptwasserpumpe des Motors 1 handelt, und ein Zwei-Wege-Ventil 4. Für den Kühlkreislauf sind wesentlichen Komponenten mit einem Verdampfer 5, einem Verdichter 6, einem Kältemittelkühler 7, einem inneren Wärmetauscher 8 und einem Expansionsventil 9 dargestellt. Der Heizwärmetauscher 2 ist durch eine By-pass-Leitung überbrückbar, wobei zwischen dieser By-pass-Leitung und dem Heizwärmetauscher 2, insbesondere Heizwärmetauscherauslaß das Zwei-Wege-Ventil 4 angeordnet ist. Durch entsprechende Umschaltung dieses Ventils lässt sich das Kühlwasser entweder durch den Heizwärmetauscher 2 oder an diesem vorbei leiten.The starting point of a corresponding air conditioning system is the conventional heating circuit of a vehicle on the one hand and the refrigerant circuit of a CO 2 air conditioning system on the other hand according to FIG 7. Figur 7 shows a possible arrangement for the heating circuit of a motor vehicle and the system scheme or the refrigerant circuit of a CO 2 air conditioning, which is designed solely for a cooling operation. The heating circuit comprises an engine 1, a heating heat exchanger 2, a circulation pump 3, which is usually the main water pump of the engine 1, and a two-way valve 4. For the refrigeration cycle are essential components with an evaporator 5, a compressor 6, a refrigerant cooler 7, an inner heat exchanger 8 and an expansion valve 9 are shown. The heating heat exchanger 2 can be bridged by a by-pass line, wherein the two-way valve 4 is arranged between this by-pass line and the heating heat exchanger 2, in particular heating heat exchanger. By appropriate switching of this valve, the cooling water can be passed either through the heating heat exchanger 2 or on this.

Ein Heizbetrieb ist mit der vorstehend beschriebenen Klimaanlage gemäß Figur 7 nicht möglich.A heating operation is with the above-described air conditioner not possible according to FIG.

Eine Klimaanlage, die außer zur Kühlung des Fahrgastraumes im Sommer auch als Heizung Verwendung finden kann, ist aus der DE 100 06 513 A1, welche die Grundlage für den Oberbegriff des Patentanspruchs 1 bildet, bekannt. Die Klimaanlage gemäß der DE 100 06 513 A1 umfaßt im wesentlichen einen Verdichter, einen Kältemittelkühler, einen inneren Wärmetauscher zwischen Kühlmittelkühler- und Verdampferseite, ein Expansionsventil und einen Verdampfer, wobei zur Umschaltung der Klimaanlage vom Kühlbetrieb in den Heizbetrieb ein mit einem motorseitigen Kühlkreislauf korrespondierender zusätzlicher Wärmetauscher integriert ist. Ferner ist dem zusätzlichen Wärmetauscher ein Expansionsventil nachgeordnet, mittels dem bei Heizbetrieb das Kältemittel auf einen niedrigeren Druck drosselbar ist.An air conditioner that except for cooling the passenger compartment in the Summer can also be used as heating is from the DE 100 06 513 A1, which forms the basis for the preamble of Patent claim 1 forms known. The air conditioning according to the DE 100 06 513 A1 essentially comprises a compressor, a Refrigerant cooler, an internal heat exchanger between coolant cooler and evaporator side, an expansion valve and a Evaporator, wherein to switch the air conditioning from the cooling mode in the heating mode with an engine-side cooling circuit integrated additional heat exchanger integrated is. Furthermore, the additional heat exchanger is an expansion valve downstream, by means of the heating mode Refrigerant can be throttled to a lower pressure.

Ferner ist aus der DE 198 18 649 A1 eine der vorstehend näher beschriebenen Klimaanlage ähnliche Klimaanlage bekannt. Auch die Klimaanlage gemäß DE 198 18 649 A1 kann sowohl zum Kühlen als auch zum Heizen verwendet werden, wobei die Betonung bei der Klimaanlage gemäß der DE 198 18 649 A1 darauf liegt, die Kaltstarteigenschaften eines Fahrzeugs zu verbessern, d.h. beim Kaltstart eines Fahrzeugs sowohl den Motor als auch den Fahrzeuginnenraum schneller aufzuheizen.Furthermore, from DE 198 18 649 A1 one of the above closer described air conditioning similar air conditioning known. Also the air conditioner according to DE 198 18 649 A1 can both for cooling as well as for heating, the emphasis being on the air conditioner according to DE 198 18 649 A1 it is the To improve cold start characteristics of a vehicle, i. at the Cold start of a vehicle both the engine and the vehicle interior to heat up faster.

Den beiden vorstehend näher beschriebenen Klimaanlagen gemäß DE 100 06 513 A1 und DE 198 18 649 A1 ist jedoch gemeinsam, daß eine Überbrückung des Expansionsventils, die notwendig ist, um einen herkömmlichen Kühlbetrieb der Klimaanlage gewährleisten zu können, relativ kompliziert gelöst ist.The two air conditioners described in more detail above However, DE 100 06 513 A1 and DE 198 18 649 A1 have in common that a bypass of the expansion valve necessary to to ensure a conventional cooling operation of the air conditioner to be able to solve is relatively complicated.

Ausgehend von diesem Stand der Technik liegt der vorliegenden Erfindung die Aufgabe zugrunde, eine konstruktiv möglichst einfache Lösung zur Überbrückung des Expansionsventils anzugeben, wobei die Klimaanlage ohne großen Aufwand von einem Kühlbetrieb in einen Heizbetrieb und umgekehrt schaltbar ist.Based on this prior art is the present Invention, the object of a structurally simple as possible Specify a solution for bridging the expansion valve, the air conditioning is easily converted by a cooling operation in a heating mode and vice versa is switchable.

Diese Aufgabe wird erfindungsgemäß durch eine Klimaanlage mit den Merkmalen des Anspruches 1 gelöst, wobei bevorzugte konstruktive Details in den Unteransprüchen beschrieben sind.This object is achieved by an air conditioner with the features of claim 1, wherein preferred constructive Details are described in the subclaims.

Ein wesentlicher Punkt der Erfindung ist es demnach, daß eine By-pass-Leitung vor einem in der der Kältemittel-Leitung angeordneten Absperrventil abzweigt und mit der Eingangsseite des Verdichters unmittelbar, d.h. unter Überbrückung des übrigen Kältemittelkreislaufs fluidverbunden ist. Damit ist eine konstruktiv einfache Lösung der der Aufgabe zugrunde liegenden Erfindung gewährleistet.An essential point of the invention is therefore that a By-pass line in front of one arranged in the refrigerant line Shut off valve and connected to the input side of Compressor immediately, i. Bridging the rest Refrigerant circuit is fluidly connected. This is a constructive simple solution of the problem underlying the invention guaranteed.

Weitere vorteilhafte Ausführungsformen ergeben sich aus den abhängigen Ansprüchen.Further advantageous embodiments will become apparent from the dependent Claims.

Nachstehend werden zwei bevorzugte Ausführungsformen der erfindungsgemäßen Klimaanlage anhand der beigefügten Zeichnung näher beschrieben. Es zeigen:

Figur 1
eine erste Ausführungsform (Schaltschema) einer erfindungsgemäßen Fahrzeugklimaanlage;
Figur 2
eine zweite Ausführungsform (Schaltschema) einer erfindungsgemäßen Fahrzeugklimaanlage; und
Figuren 3 bis 6
weitere Abwandlungen (Schaltschemen) einer erfindungsgemäßen Fahrzeugklimaanlage.
Hereinafter, two preferred embodiments of the air conditioner according to the invention will be described with reference to the accompanying drawings. Show it:
FIG. 1
a first embodiment (circuit diagram) of a vehicle air conditioning system according to the invention;
FIG. 2
a second embodiment (circuit diagram) of a vehicle air conditioning system according to the invention; and
FIGS. 3 to 6
Further modifications (schematics) of a vehicle air conditioning system according to the invention.

Die Klimaanlage gemäß Figur 1 ist gegenüber dem Stand der Technik nach Figur 3 dahingehend modifiziert, daß ein Heizbetrieb mit der dann als Wärmepumpe arbeitenden Klimaanlage möglich ist. Zu diesem Zweck ist ein zusätzlicher Wärmetauscher 10 vorgesehen, der zum Enthitzen des gasförmigen Kältemittels und zum Übertragen der Wärme an einen Kühlwasserkreislauf eingebunden ist. Der Kühlwasserkreislauf ist mit der Bezugsziffer 17 gekennzeichnet. Im zusätzlichen Wärmetauscher 10 erfolgt also ein Wärmeaustausch zwischen dem Kältemittelkreislauf einerseits und motorseitigem Kühlwasserkreislauf andererseits. Das auf hohe Temperatur erhitzte Kältemittel, nämlich CO2, stammt von dem Wärmetauscher 10 vorgeschalteten Verdichter 6. Dem zusätzlichen Wärmetauscher 10 ist ein Expansionsventil 14 nachgeordnet, mittels dem bei Heizbetrieb das Kältemittel auf einen niedrigeren Druck drosselbar ist. Konkret befindet sich das Expansionsventil 14 in einer By-pass-Leitung, die von der Kältemittel-Leitung 13 zwischen zusätzlichem Wärmetauscher 10 und Kältemittelkühler 7 abzweigt. Diese By-pass-Leitung ist mit der Bezugsziffer 15 gekennzeichnet. Sie ist parallel zur erwähnten Kühlmittel-Leitung unter Überbrückung eines in dieser angeordneten Absperrventils 11 geschaltet. Das Absperrventil 11 dient zur Absperrung des freien Kältemittel-Durchgangs zwischen dem zusätzlichen Wärmetauscher 10 und Kältemittelkühler 7. In der Sperrstellung des Ventils 11 ist das Expansionsventil 14 wirksam, durch das der Druck des Kältemittels soweit abgedrosselt wird, daß der im Klimafall als Kältemittelkühler dienende Wärmetauscher 7 im Wärmepumpenbetrieb als Verdampfer Umgebungswärme aufnimmt. The air conditioning system of Figure 1 is compared to the prior art of Figure 3 modified to the effect that a heating operation with the then operating as a heat pump air conditioning is possible. For this purpose, an additional heat exchanger 10 is provided, which is integrated for deheating the gaseous refrigerant and for transferring the heat to a cooling water circuit. The cooling water circuit is identified by the reference numeral 17. In the additional heat exchanger 10 so there is a heat exchange between the refrigerant circuit on the one hand and motor-side cooling water circuit on the other. The heated to high temperature refrigerant, namely CO 2 , comes from the heat exchanger 10 upstream compressor 6. The additional heat exchanger 10 is followed by an expansion valve 14, by means of which the refrigerant can be throttled to a lower pressure during heating operation. Concretely, the expansion valve 14 is in a by-pass line, which branches off from the refrigerant line 13 between the additional heat exchanger 10 and the refrigerant cooler 7. This by-pass line is identified by the reference numeral 15. It is connected in parallel to the aforementioned coolant line while bridging a shut-off valve 11 arranged in the latter. The shut-off valve 11 serves to shut off the free refrigerant passage between the additional heat exchanger 10 and refrigerant radiator 7. In the blocking position of the valve 11, the expansion valve 14 is effective, by which the pressure of the refrigerant is throttled so far that serving as a refrigerant radiator in the climate case heat exchanger 7 absorbs heat in heat pump mode as an evaporator ambient heat.

Darüber hinaus sei erwähnt, daß im Kältemittelkreislauf zwischen dem inneren Wärmetauscher 8 und dem diesem nachgeordneten Verdampfer 5 ein weiteres Expansionsventil 9 angeordnet ist, das bei Bedarf, nämlich Heizbetrieb durch eine By-pass-Leitung 18 mit Absperrventil 12 überbrückbar ist. Im Heizbetrieb wird das üblicherweise wirksame Expansionsventil 9 durch die By-pass-Leitung 18 mit geöffnetem Absperrventil 12 überbrückt.In addition, it should be mentioned that in the refrigerant circuit between the inner heat exchanger 8 and this downstream Evaporator 5 another expansion valve 9 is arranged, if necessary, namely heating operation by a by-pass line 18 with shut-off valve 12 can be bridged. In heating mode is the usually effective expansion valve 9 through the by-pass line 18 bridged with open shut-off valve 12.

Die Betriebsweise im Heizbetrieb ist wie folgt:
Der Verdichter 6 verdichtet das Kältemittel, nämlich CO2, auf einen hohen Enddruck von etwa 80-120 Bar. Die Verdichtungsendtemperaturen werden absichtlich hoch gehalten, so daß in dem zusätzlichen Wärmetauscher 10 ausreichend Wärme an den motorseitigen Heizwasserkreislauf 17 übertragen werden kann, die dann über den Heizwärmetauscher 2 der Fahrgastzelle zugeführt wird. Das Kältemittel, d.h. CO2, wird durch das dem zusätzlichen Wärmetauscher 10 nachgeordnete Expansionsventil 14 auf eine niedrigeren Druck von z.B. etwa 20 Bar in das Nassdampfgebiet gedrosselt und verdampft im Kältemittelkühler 7 bei niedrigeren Temperaturen. Dabei nimmt das Kältemittel Umweltwärme auf. Der innere Wärmetauscher 8 und der Verdampfer 5 werden ohne nennenswerten Wärmeaustausch durchströmt. Das Ventil 12 wird praktisch ohne Druckverlust und damit ohne Druckänderung durchströmt.The mode of operation in heating mode is as follows:
The compressor 6 compresses the refrigerant, namely CO 2 , to a high final pressure of about 80-120 bar. The compression end temperatures are deliberately kept high, so that sufficient heat can be transferred to the motor side heating water circuit 17 in the additional heat exchanger 10, which then the heating heat exchanger 2 is supplied to the passenger compartment. The refrigerant, ie CO 2 , is throttled by the additional heat exchanger 10 downstream expansion valve 14 to a lower pressure of, for example, about 20 bar in the wet steam area and evaporates in the refrigerant cooler 7 at lower temperatures. The refrigerant absorbs environmental heat. The inner heat exchanger 8 and the evaporator 5 are flowed through without appreciable heat exchange. The valve 12 is flowed through virtually without pressure loss and thus without pressure change.

Betriebsweise im Kühlbetrieb:
Im Verdampfer 5 verdampft das Kältemittel und nimmt so Wärme aus der Umgebungsluft auf, die der Fahrgastzelle zugeführt wird. Im inneren Wärmetauscher 8 wird das Sauggas überhitzt und dem Verdichter 6 zugeführt. Das Kältemittel wird auf einen Druck von z.B. 70-120 Bar verdichtet und erreicht eine Verdichtungsendtemperatur von bis zu und über 150 °C. Das Kältemittel wird anschließend im zusätzlichen Wärmetauscher 10 enthitzt und strömt durch das geöffnete Absperrventil 11 hindurch in den nachgeordneten Kältemittelkühler 7, und zwar energetisch bereits vorgekühlt, so daß im Kältemittelkühler 7 lediglich eine anteilige Kühlung des Kältemittels erfolgen muß. Das Kältemittel wird dann im inneren Wärmetauscher weiter unterkühlt und Expansionsventil 9 auf den Verdampfungsdruck gedrosselt. Beim Kühlbetrieb ist das Absperrventil 12 in der By-pass-Leitung 18 geschlossen. Energetisch vorteilhaft stehen für die Kühlung des Kältemittels bzw. CO2-Gases sowohl der zusätzliche Wärmetauscher 10 als auch der Kältemittelkühler 7 zur Verfügung. Damit ist der Kühlbetrieb energetisch günstiger als bei einem reinen Kühlkreislauf nach Figur 3. Dieser Nebeneffekt kann dazu genutzt werden, einen kostengünstigeren Kältemittelkühler einzusetzen oder die energetische Effizienz der Gesamtanlage zu verbessern. Die Wärme, die vom zusätzlichen Wärmetauscher 10 an den Kühlwasserkreislauf 17 übertragen wird, lässt sich im By-pass um den Heizwärmetauscher 2 unmittelbar dem Motor 1 zuführen. Im Lehrlauf, bei niedrigen Lasten und im Warmlauf dient diese Wärme dazu, den Motor auf energetisch günstiger Betriebstemperatur zu halten und damit Kraftstoff einzusparen. Ist der Motor betriebswarm, wird die Wärme über den hier nicht näher dargestellten Motorkühler abgeführt.Operating mode in cooling mode:
In the evaporator 5, the refrigerant evaporates and thus absorbs heat from the ambient air, which is supplied to the passenger compartment. In the inner heat exchanger 8, the suction gas is superheated and fed to the compressor 6. The refrigerant is compressed to a pressure of eg 70-120 bar and reaches a final compression temperature of up to and above 150 ° C. The refrigerant is then re-enticed in the additional heat exchanger 10 and flows through the open shut-off valve 11 into the downstream refrigerant cooler 7, namely pre-cooled energetically, so that only a proportionate cooling of the refrigerant must be carried out in the refrigerant cooler 7. The refrigerant is then further subcooled in the inner heat exchanger and throttled expansion valve 9 to the evaporation pressure. During cooling operation, the shut-off valve 12 in the by-pass line 18 is closed. In terms of energy, both the additional heat exchanger 10 and the refrigerant cooler 7 are available for cooling the refrigerant or CO 2 gas. Thus, the cooling operation is energetically cheaper than in a pure cooling circuit of Figure 3. This side effect can be used to use a cheaper refrigerant radiator or to improve the energy efficiency of the entire system. The heat that is transferred from the additional heat exchanger 10 to the cooling water circuit 17, can be in the bypass pass to the heating heat exchanger 2 directly to the engine 1. During warm-up, at low loads and during warm-up, this heat serves to keep the engine at an energy-efficient operating temperature and thereby save fuel. If the engine is warm, the heat is dissipated via the engine radiator not shown here.

Damit ist solch ein dem Verdichter nachgeschalteter, kühlwasserbeaufschlagter Wärmetauscher auch für eine CO2-Klimaanlage ohne Heizfunktion vorteilhaft. Neben dem Wärmetauscher, der als Enthitzer eingesetzt wird, sind dann keine zusätzlichen Ventile erforderlich. Diese Version wird als erfindungsgemäße Variante betrachtet und beansprucht.Thus, such a compressor downstream, Kühlwasserbeaufschlagter heat exchanger is also advantageous for a CO 2 air conditioning without heating function. In addition to the heat exchanger, which is used as a desuperheater, then no additional valves are required. This version is considered and claimed as a variant of the invention.

Wir der Motor an seinem thermischen Grenzbereich betrieben, was bei hohen Fahrgeschwindigkeiten unter hoher Last der Fall ist, so wird der Kältemittelkühler 7 luftseitig hinreichend gut durchströmt, so daß der Verdichtungsenddruck niedrig genug ist und die Verdichtungsendtemperatur ebenfalls niedrig ist. In diesem Fall wird vom zusätzlichen Wärmetauscher 10 an den dann ohnehin heißen Kühlwasserkreislauf keine Wärme mehr übertragen, da die Temperaturdifferenz gering oder sogar negativ ist. Der Motor wird dann thermisch nicht mehr zusätzlich belastet. Der Motorkühler braucht daher nicht größer dimensioniert werden.We operated the engine at its thermal boundary area, which at high speeds under high load, so the refrigerant cooler 7 air side sufficiently well flows through, so that the compression end pressure is low enough and the compression end temperature is also low. In This case is from the additional heat exchanger 10 to the then anyway, the cooling water circuit is no longer transmitting any heat, because the temperature difference is low or even negative. Of the Engine is then no longer charged thermally. Of the Engine radiator therefore does not need to be sized larger.

Restwärme, die im Heizbetrieb nicht an die Fahrgastzelle übertragen wird, dient bei kaltem Motor dazu, diesen zusätzlich zu erwärmen und in einen energetisch günstigen Betriebspunkt zu bringen.Residual heat that does not transfer to the passenger compartment in heating mode is used in cold engine, this in addition to heat up and into an energetically favorable operating point bring.

Die Variante gemäß Figur 2 zeichnet sich dadurch aus, daß von der Kältemittel-Leitung 13 zwischen zusätzlichem Wärmetauscher 10 und Kältemittelkühler 7 eine By-pass-Leitung 15 abzweigt, und zwar vor einem in der erwähnte Kältemittel-Leitung 13 angeordneten Absperrventil 11. Die By-pass-Leitung 15 ist mit der Eingangsseite des Verdichters 6 unmittelbar, d.h. unter Überbrückung des übrigen Kühlmittelkreislaufs fluidverbunden.The variant according to Figure 2 is characterized in that of the refrigerant line 13 between additional heat exchanger 10 and refrigerant cooler 7 branches off a by-pass line 15, in front of a disposed in the mentioned refrigerant line 13 Shut-off valve 11. The by-pass line 15 is connected to the Input side of the compressor 6 directly, i. under bridging the other coolant circuit fluidly connected.

Bei dieser Ausführungsform ist es nicht erforderlich, das weitere Expansionsventil 9 zwischen innerem Wärmetauscher 8 und Verdampfer 5 zu überbrücken.In this embodiment, it is not necessary to further Expansion valve 9 between the inner heat exchanger 8 and Evaporator 5 to bridge.

In der By-pass-Leitung 15 ist ein Expansionsventil 16 angeordnet. Die Ausführungsform nach Figur 2 zeichnet sich also durch einen Heißgas-By-pass-Kreislauf im Heizbetrieb aus bedingt durch die unmittelbare Verbindung zwischen dem Kältemittel-Ausgang des zusätzlichen Wärmetauschers 10 und dem Eingang des Verdichters 6. Die im zusätzlichen Wärmetauscher 10 abgegebene Leistung entspricht der vom Verdichter 6 aufgenommenen Leistung. Ein Wärmepumpenbetrieb durch Aufnahme zusätzlicher Umweltwärme liegt nicht vor. Das Expansionsventil 16 muß beim normalen Kühlbetrieb geschlossen sein. Es im übrigen denkbar, die By-pass-Leitung 15 bei der Ausführungsform nach Figur 2 als Kapillare auszuführen, die eine hinreichende Drosselwirkung besitzt. In diesem Fall würde es genügen, für das Ventil 16 ein einfaches Absperrventil zu verwenden. Wie bereits erwähnt, kann auf das Absperrventil 12 zur Umgehung des Expansionsventils 9 zwischen innerem Wärmetauscher 8 und Verdampfer 5 verzichtet werden. Vereisungsprobleme, die luftseitig am Kältemittelkühler 7 nicht völlig auszuschließen sind, können mit dieser Schaltung vorteilhaft gegenüber anderen Schaltungen vermieden werden. Weiterhin können Probleme durch Vereisungen und Restfeuchte am Verdampfer 5 vermieden werden.In the by-pass line 15, an expansion valve 16 is arranged. The embodiment of Figure 2 is characterized by a hot gas bypass circuit in heating operation conditionally through the direct connection between the refrigerant outlet the additional heat exchanger 10 and the input of the Compressor 6. The votes in the additional heat exchanger 10 Power corresponds to the power absorbed by the compressor 6. A heat pump operation by absorbing additional environmental heat not available. The expansion valve 16 must during be closed normal cooling operation. Incidentally, it is conceivable the by-pass line 15 in the embodiment of Figure 2 as Capillary perform that has a sufficient throttle effect. In this case, it would suffice for the valve 16 a easy to use shut-off valve. As already mentioned, can on the shut-off valve 12 for bypassing the expansion valve. 9 between inner heat exchanger 8 and evaporator 5 is omitted become. Icing problems, the air side of the refrigerant radiator 7 can not be completely ruled out, can with this circuit be advantageously avoided over other circuits. Furthermore, problems due to icing and residual moisture at the Evaporator 5 can be avoided.

Es sei an dieser Stelle noch erwähnt, daß Wärmepumpenschaltungen, die auf einer einfachen Kreislaufumkehr beruhen, häufig zu Problemen mit Restfeuchte auf der Verdampferoberfläche führen, die vom Klimabetrieb herrührt. Bei Umschaltung von Klima- bzw. Kühlbetrieb in den Heizbetrieb wird diese Feuchte dann von dem nun als Heizung verwendeten Verdampfer 5 der Klimaanlage freigesetzt und kann zu plötzlichem sicherheitsrelevantem Beschlag an den Scheiben des Kraftfahrzeuges führen. Man nennt dies auch "flash-fogging". Auch sind Geruchsbelästigungen denkbar.It should be mentioned at this point that heat pump circuits, which are based on a simple cycle reversal, often too Cause problems with residual moisture on the evaporator surface, which comes from the air conditioning operation. When switching from climate or Cooling operation in the heating mode, this moisture is then from the now used as a heater evaporator 5 of the air conditioning released and can cause sudden safety-related fogging on the windows of the motor vehicle. This is also called "Flash fogging". Also odor nuisances are conceivable.

Bei den hier beschriebenen Anlagen bzw. Schaltungen sind die vorgenannten Probleme ausgeschlossen, da der Verdampfer 5 stets kühl gehalten und die Wärme im wasserbeaufschlagten Heizwärmetauscher übertragen werden. Je nach Ausführung und Ansteuerung der Ventile lässt sich bei den beschriebenen Schaltungen auch ganz gezielt ein Entfeuchtungsbetrieb realisieren, bei dem im Verdampfer 5 entfeuchtet und Heizwärmetauscher 2 nachgeheizt wird.In the plants or circuits described here are the aforementioned problems excluded because the evaporator 5 always kept cool and the heat in wasserbeaufschlagten heating heat exchanger be transmitted. Depending on the version and control the valves can be in the circuits described also specifically to realize a dehumidifying operation in which the Evaporator 5 dehumidified and reheated 2 heat exchanger becomes.

Es sei ferner als weiterer Vorteil erwähnt, daß anders als bei bekannt gewordenen Wärmepumpen-Schaltungen mit dem Kältemittel CO2, die das Kühlwasser des Motors als Wärmequelle verwenden, dem Kühlwasser keine Wärme entzogen wird. Damit heizt sich der Motor schnellstmöglich auf und auf die Zuheizung kann vorteilhaft frühzeitig verzichtet werden. It should also be mentioned as a further advantage that, unlike in known heat pump circuits with the refrigerant CO 2 , which use the cooling water of the engine as a heat source, the cooling water no heat is removed. This heats up the engine as quickly as possible and the additional heating can advantageously be dispensed with at an early stage.

Als vorteilhaft zur schnelleren Aufheizung der Fahrgastkabine hat sich die zeitweilige Trennung vom Motor- und Heißwasserkreislauf z.B. nach Fig. 3 oder 4 erwiesen. Die Wärme wird von der Wärmepumpe bzw. der Heißgas-by-pass-Schaltung nur zur Aufheizung des kleinen Heizwasser-Kreislaufs verwendet. Ein schnelles Aufheizen ist die Folge. Ist die Kühlwassertemperatur hinreichend angestiegen, wird die Anlage wieder umgeschaltet und die Motorabwärme wird zum Heizen verwendet. Diese vorgenannte Umschaltung wird durch eine by-pass-Schaltung 19 im Heizwasser-Kreislauf zwischen Motor 1 und Pumpe 3 einerseits und der Rücklaufleitung zwischen Heizwärmetauscher 2 und Motor 1 andererseits erhalten, wobei entweder an letztgenannter Abzweigung ein Zwei-Wege-Ventil 20 (Fig. 3) oder an erstgenanntem Anschluß ein Zwei-Wege-Ventil 21 (Fig. 4) vorgesehen ist, mit dem die vorbeschriebene Umschaltung möglich ist.As advantageous for faster heating of the passenger cabin has the temporary separation from the engine and hot water cycle e.g. proved according to Fig. 3 or 4. The heat will from the heat pump or the hot gas-by-pass circuit only to Heating of the small heating water circuit used. One quick heating up is the result. Is the cooling water temperature sufficiently increased, the system is switched again and the engine waste heat is used for heating. These aforementioned Switching is done by a by-pass circuit 19 in the Heating water circuit between engine 1 and pump 3 on the one hand and the return line between the heat exchanger 2 and engine 1 on the other hand, either at the last-mentioned branch a two-way valve 20 (Figure 3) or the former Connection a two-way valve 21 (Fig. 4) is provided with the above-described switching is possible.

Die erwähnten Absperrventile können natürlich auch in Zwischenstellungen gebracht werden abhängig vom gewünschten Betriebszustand.The aforementioned shut-off valves can of course also in intermediate positions be brought depending on the desired operating condition.

Zur sicheren Vermeidung von Problemen bei der Durchströmung des Verdampfers 5 unter Heizbetrieb bei der Ausführungsform gemäß Fig. 1, ist in Fig. 5 und 6 eine Umgehung des Verdampfers 5 vorgesehen. Die by-pass-Leitung 18 mit by-pass-Ventil 12 überbrückt entweder den inneren Wärmetauscher 8 und Verdampfer 5 (Fig. 5) oder das Expansionsventil und Verdampfer 5 (Fig. 6), also in jedem Fall den Verdampfer 5.To safely avoid problems with the flow through the Evaporator 5 under heating operation in the embodiment according to FIG. 1, in FIGS. 5 and 6, is a bypass of the evaporator 5 intended. The by-pass line 18 with by-pass valve 12 bridged either the inner heat exchanger 8 and evaporator. 5 (Figure 5) or the expansion valve and evaporator 5 (Figure 6), So in any case, the evaporator. 5

Sämtliche in den Anmeldungsunterlagen offenbarten Merkmale werden als erfindungswesentlich beansprucht, soweit sie einzeln oder in Kombination gegenüber dem Stand der Technik neu sind. All features disclosed in the application documents become as claimed essential to the invention, as far as they individually or in combination with the prior art.

Bezugszeichenreference numeral

11
Motorengine
22
Heizwärmetauscherheating heat exchanger
33
Pumpepump
44
Zwei-Wege-VentilTwo-way valve
55
VerdampferEvaporator
66
Verdichtercompressor
77
Wärmetauscher bzw. KältemittelkühlerHeat exchanger or refrigerant cooler
88th
innerer Wärmetauscherinternal heat exchanger
99
Expansionsventilexpansion valve
1010
zusätzlicher Wärmetauscheradditional heat exchanger
1111
Absperrventilshut-off valve
1212
Absperrventilshut-off valve
1313
Kältemittel-LeitungRefrigerant piping
1414
Expansionsventilexpansion valve
1515
By-pass-LeitungBy-pass line
1616
Expansionsventilexpansion valve
1717
KühlwasserkreislaufCooling water circuit
1818
By-pass-LeitungBy-pass line
1919
By-pass-LeitungBy-pass line
2020
Zwei-Wege-VentilTwo-way valve
2121
Zwei-Wege-VentilTwo-way valve

Claims (3)

  1. Vehicle air-conditioning system, especially a CO2 air-conditioning system, the coolant circuit of which comprises the following components:
    compressor (6),
    coolant cooler (7),
    internal heat exchanger (8) between the coolant cooler side and evaporator side,
    expansion valve (9) and
    evaporator (5), wherein
    there is integrated, for switching over the air-conditioning system from cooling operation to heating operation, an additional heat exchanger (10) associated with an engine-side cooling circuit (17), an expansion valve (14, 16) being arranged downstream of the additional heat exchanger (10), by means of which expansion valve the coolant can be throttled to a lower pressure during heating operation, and wherein
    the expansion valve (14; 16) is part of a by-pass line (15) branching off from the coolant line (13),
    characterised in that
    the additional heat exchanger (10) is integrated between the compressor (6) and the coolant cooler (7),
    the by-pass line (15) branches off, from the coolant line, between the additional heat exchanger (10) and the coolant cooler (7), and
    the by-pass line (15) branches off before a shut-off valve (11) arranged in the coolant line (13) and is in fluid communication with the inlet side of the compressor (6) directly, that is to say shunting the rest of the coolant circuit.
  2. Air-conditioning system according to claim 1,
    characterised in that
    a further expansion valve (9) is arranged in the coolant circuit between the internal heat exchanger (8) and the evaporator (5), which further expansion valve is arranged to be shunted, when required, especially during heating operation, by a by-pass line (18) having a shut-off valve (12).
  3. Air-conditioning system according to one of claims 1 or 2,
    characterised in that
    an engine-side heating heat exchanger (2) is arranged to be shunted by a by-pass line, the redirection of the cooling medium, especially cooling water, being effected by means of a two-way valve (4) arranged between the by-pass line and the heating heat exchanger (2), especially the heating heat exchanger inlet or outlet.
EP03003752A 2002-02-20 2003-02-19 Vehicle air conditioning system, especially CO2-air conditioning system Expired - Lifetime EP1338449B1 (en)

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DE10207128 2002-02-20
DE10207128A DE10207128A1 (en) 2002-02-20 2002-02-20 Vehicle air conditioning system, especially carbon dioxide unit, has additional heat exchanger and pressure reducing throttle valve

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Families Citing this family (35)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7032119B2 (en) * 2000-09-27 2006-04-18 Amphus, Inc. Dynamic power and workload management for multi-server system
JP3736847B2 (en) * 2002-12-06 2006-01-18 松下電器産業株式会社 Air conditioning apparatus and air conditioning method
ES2293052T3 (en) * 2002-12-20 2008-03-16 BEHR GMBH & CO. KG AIR CONDITIONING INSTALLATION FOR A VEHICLE AND ASSOCIATED OPERATING PROCEDURE.
JP2004217087A (en) * 2003-01-15 2004-08-05 Calsonic Kansei Corp Vehicular air conditioner
JP2004268752A (en) * 2003-03-10 2004-09-30 Denso Corp Heat management system
JP2005263200A (en) * 2004-02-18 2005-09-29 Denso Corp Air conditioner for vehicle
DE102004024255A1 (en) * 2004-05-15 2005-12-01 Modine Manufacturing Co., Racine Arrangement in a refrigerant circuit and working method
DE102005001231A1 (en) * 2005-01-11 2006-07-13 Daimlerchrysler Ag Air conditioning for motor vehicles
DE602007001038D1 (en) 2006-01-31 2009-06-18 Sanyo Electric Co air conditioning
US20090159259A1 (en) * 2006-06-30 2009-06-25 Sunil Kumar Sinha Modular heat pump liquid heater system
US7543456B2 (en) * 2006-06-30 2009-06-09 Airgenerate Llc Heat pump liquid heater
NL1032852C2 (en) * 2006-11-10 2008-05-14 Antonie Bonte Heat pump installation with compressor, includes internal heat exchangers arranged in series for heating suction gas
JP4505510B2 (en) * 2007-02-20 2010-07-21 カルソニックカンセイ株式会社 Vehicle air conditioning system
US8517087B2 (en) * 2007-02-20 2013-08-27 Bergstrom, Inc. Combined heating and air conditioning system for vehicles
US8011598B2 (en) * 2007-04-18 2011-09-06 Delphi Technologies, Inc. SOFC power system with A/C system and heat pump for stationary and transportation applications
DE102009042774A1 (en) * 2009-09-25 2011-03-31 Behr Gmbh & Co. Kg System for a motor vehicle for heating and / or cooling a battery and a motor vehicle interior
JP2011126491A (en) * 2009-12-21 2011-06-30 Calsonic Kansei Corp Vehicular air conditioner
DE102009060860B4 (en) 2009-12-30 2024-06-27 Konvekta Aktiengesellschaft Air conditioning system for a vehicle and method for controlling the temperature
DE102010000990B4 (en) * 2010-01-19 2018-01-11 Hanon Systems Method for operating an air conditioning system
WO2012114422A1 (en) * 2011-02-21 2012-08-30 株式会社日立製作所 Vehicle air conditioning system
DE102012215971A1 (en) * 2012-09-10 2014-05-28 Bayerische Motoren Werke Aktiengesellschaft Method for thermally conditioning an internal combustion engine and / or a passenger compartment of a vehicle and vehicle
DE102012222594B4 (en) 2012-12-10 2018-05-17 Bayerische Motoren Werke Aktiengesellschaft Method for operating a refrigerant circuit as a heat pump and as a heat pump operable refrigerant circuit
JP6011375B2 (en) * 2013-02-01 2016-10-19 株式会社デンソー Refrigeration cycle equipment
KR101416416B1 (en) * 2013-06-03 2014-07-09 현대자동차 주식회사 Heating system for electric vehicle
US9630474B2 (en) 2013-10-29 2017-04-25 Denso International America, Inc. Thermostatic controlled heat pump water circuit
DE102013114081A1 (en) * 2013-12-16 2015-06-18 Valeo Klimasysteme Gmbh Vehicle air conditioning
DE102014113526A1 (en) * 2014-09-19 2016-03-24 Halla Visteon Climate Control Corporation Air conditioning system for a motor vehicle
FR3030700B1 (en) * 2014-12-18 2019-03-22 Valeo Systemes Thermiques AIR CONDITIONING CIRCUIT FOR A MOTOR VEHICLE
WO2016185243A1 (en) * 2015-05-15 2016-11-24 Carrier Corporation Staged expansion system and method
FR3055249B1 (en) * 2016-08-30 2018-09-14 Valeo Systemes Thermiques INDIRECT INDIRECT AIR CONDITIONING CIRCUIT FOR A MOTOR VEHICLE AND METHOD OF OPERATING THE SAME
FR3057211B1 (en) * 2016-10-12 2020-09-04 Valeo Systemes Thermiques PROCESS FOR REGULATING A HEATING, VENTILATION AND / OR AIR CONDITIONING LOOP
CN108248331B (en) * 2016-12-29 2023-11-14 比亚迪股份有限公司 Heat pump air conditioning system and electric automobile
KR102609407B1 (en) * 2017-08-21 2023-12-04 한온시스템 주식회사 Air conditioning system for automotive vehicles and control method using the same
KR20190120936A (en) * 2018-04-17 2019-10-25 한온시스템 주식회사 Heat management system of vehicle
CN108725138B (en) * 2018-08-14 2023-09-22 协众国际热管理系统(江苏)股份有限公司 Carbon dioxide heat pump thermal management system for new energy automobile and working method thereof

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3446032A (en) * 1967-03-10 1969-05-27 Edward W Bottum Heat exchanger
JPH06323637A (en) * 1993-05-18 1994-11-25 Mitsubishi Heavy Ind Ltd Refrigerating cycle
JPH1076841A (en) * 1996-09-06 1998-03-24 Calsonic Corp Heat pump type air conditioner for automobile
JP3952545B2 (en) * 1997-07-24 2007-08-01 株式会社デンソー Air conditioner for vehicles
DE19818649A1 (en) * 1998-04-25 1999-10-28 Behr Gmbh & Co Vehicle air-conditioning system
DE19850829C1 (en) * 1998-11-04 2000-03-16 Valeo Klimasysteme Gmbh Cooling-heating circuit for motor vehicle has temperature increasing and/or reducing devices associated with cooling-heating circuit at least partly according to their operating states, especially temperature
JP2000211350A (en) * 1999-01-27 2000-08-02 Japan Climate Systems Corp Vehicle air-conditioner
DE10006513B4 (en) * 2000-02-15 2014-12-24 Behr Gmbh & Co. Kg Air conditioning system for a motor vehicle with heat pump and / or reheat mode
DE10029934A1 (en) * 2000-06-17 2002-01-03 Behr Gmbh & Co Air conditioning with air conditioning and heat pump mode
US6386277B1 (en) * 2001-04-24 2002-05-14 Modine Manufacturing Company Heat exchanger header construction
DE10123830A1 (en) * 2001-05-16 2002-11-28 Bosch Gmbh Robert Vehicle air conditioning system uses a heat pump action with the evaporator as the heat source, in the heating mode, for a rapid heating of the interior without loss and heating of the motor to its working temperature

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US20030177778A1 (en) 2003-09-25
DE10207128A1 (en) 2003-08-21
US6913067B2 (en) 2005-07-05
EP1338449A1 (en) 2003-08-27

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